Compressor

ABSTRACT

A compressor includes fixed scroll (6) and revolving scroll (7) configuring compression mechanism (2), compression chamber (9), intake chamber (11), discharge port (12), muffler (16), and heat-insulating member (24) provided between fixed scroll (6) and muffler (16). After a refrigerant gas taken into intake chamber (11) is compressed by revolving scroll (7) revolving and compression chamber (9) moving while changing a volume of compression chamber (9), the refrigerant gas is discharged from discharge port (12). The refrigerant gas discharged from discharge port (12) is discharged into muffler space (14) formed by muffler (16). Heat-insulating member (24) includes heat-insulating member discharge port (25), lead valve (13), and recess (27).

TECHNICAL FIELD

The present disclosure relates to a compressor used for a cooling device such as a heating-cooling air conditioner and a refrigerator, a heat pump type water heater, and the like.

BACKGROUND ART

Conventionally, a hermetic compressor used for a cooling device, a water heater, and the like plays a role of compressing a refrigerant gas returned from a refrigeration cycle in a compression mechanism and sending the refrigerant gas to the refrigeration cycle. The refrigerant gas returned from the refrigeration cycle is supplied to a compression chamber formed in the compression mechanism through an intake route. After that, the refrigerant gas that has been compressed to have a high temperature and high pressure is discharged from the compression mechanism into an airtight container and sent from a discharge pipe provided in the airtight container to the refrigeration cycle (for example, see PTL 1).

FIG. 5 is a sectional view showing the compression mechanism of the conventional scroll compressor described in PTL 1.

A low-temperature and low-pressure refrigerant gas passes through intake pipe 101, is led to the intake chamber of fixed scroll 102, and compressed by a volume change of compression chamber 103 to have a high temperature and high pressure. After that, the high-temperature and high-pressure refrigerant gas passes through discharge port 104 at an upper part of fixed scroll 102, is discharged into muffler space 106 configured with fixed scroll 102 and muffler 105 covering the upper part of fixed scroll 102, and is sent from discharge pipe 108 to the refrigeration cycle through an inside of airtight container 107 from muffler space 106.

CITATION LIST Patent Literature

PTL 1: Unexamined Japanese Patent Publication No. 2007-247601

SUMMARY OF THE INVENTION

In the compressor having the configuration of FIG. 5, however, the low-temperature refrigerant led to the intake chamber of fixed scroll 102 is affected by heat (for example, being heated) of the highest-temperature and highest-pressure refrigerant gas discharged from discharge port 104 at the upper part of fixed scroll 102 into muffler space 106.

As a result, the refrigerant gas expands when being confined in compression chamber 103. Accordingly, a circulation amount of the refrigerant gas decreases.

Moreover, since a refrigerant gas that is being compressed in compression chamber 103 passes through fixed scroll 102 from muffler space 106, the refrigerant gas is also affected by heat of the high-temperature and high-pressure refrigerant gas. As a result, the refrigerant gas expands, and a compression loss of a refrigerant increases.

The present disclosure solves the conventional problems described above, and an object of the present disclosure is to provide a highly efficient compressor through suppression of a decrease in a circulation amount of a refrigerant and reduction of a compression loss of the refrigerant.

The compressor of the present disclosure includes a fixed scroll and a revolving scroll configuring a compression mechanism, a compression chamber formed between the fixed scroll and the revolving scroll, an intake chamber provided on an outer circumferential side of the fixed scroll, a discharge port provided in a central part of the fixed scroll, a muffler provided to cover the discharge port at an upper part of the fixed scroll, and a heat-insulating member provided between the fixed scroll and the muffler. After a refrigerant gas taken into the intake chamber is compressed by the revolving scroll revolving and the compression chamber moving while changing a volume of the compression chamber, the refrigerant gas is discharged from the discharge port. The refrigerant gas discharged from the discharge port is discharged into a muffler space formed by the muffler. The heat-insulating member includes a heat-insulating member discharge port provided in a portion facing the discharge port, a lead valve provided on a surface, of the heat-insulating member, on a side opposite to a side facing the fixed scroll, and a recess provided on the surface, of the heat-insulating member, facing the fixed scroll and provided in a 360-degree area in a circumferential direction facing the intake chamber.

By so doing, a high-temperature and high-pressure refrigerant gas compressed in the compression chamber is discharged from the heat-insulating member discharge port into the muffler space. As a result, the high-temperature and high-pressure refrigerant gas discharged into the muffler space gives an influence of heat from the muffler space into the intake chamber. However, against the influence of heat, the heat-insulating member provided between the fixed scroll and the muffler serves as a heat-insulating layer. Further, since a refrigerant gas and oil in the refrigerant gas intrude into the recess provided in the heat-insulating member and stay in the recess, the recess serves as a second heat-insulating layer. These double heat-insulating layers suppress the influence of heat from the muffler space through which a highest-temperature and highest-pressure refrigerant passes into the intake chamber and compression chamber before compression starts when the fixed scroll has a lowest temperature. In particular, the recess is provided in a 360-degree area, of the heat-insulating member, in a circumferential direction on a surface facing the fixed scroll. Therefore, the influence of heat from the muffler space is extensively and effectively suppressed over a substantially whole area of the intake chamber and the compression chamber continued to the intake chamber. In addition, together with the muffler space, the heat-insulating member suppresses the influence of heat upon the compression chamber from a high-temperature refrigerant in a space inside a container above the muffler space. Accordingly, since an increase in a temperature of the refrigerant is strongly suppressed (for example, blocked), a decrease in a circulation amount of the refrigerant is prevented, and an increase in a compression loss of the refrigerant is suppressed. As a result, a highly efficient compressor can be achieved.

According to the present disclosure, an increase in a temperature of a refrigerant is suppressed, a decrease in a circulation amount of the refrigerant is prevented, and an increase in a compression loss of the refrigerant is suppressed. As a result, a highly efficient compressor can be provided.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a view showing one example of a cross section of a compressor according to a first exemplary embodiment of the present disclosure viewed from a side.

FIG. 2 is a view showing one example of a main part of the compressor.

FIG. 3 is a plan view showing one example of a configuration of the compressor.

FIG. 4 is a view showing one example of a heat-insulating member of the compressor.

FIG. 5 is a view showing one example of a cross section of a scroll compressor in a comparative example viewed from a side.

DESCRIPTION OF EMBODIMENT

The compressor of a first aspect the present disclosure includes a fixed scroll and a revolving scroll configuring a compression mechanism, a compression chamber formed between the fixed scroll and the revolving scroll, an intake chamber provided on an outer circumferential side of the fixed scroll, a discharge port provided in a central part of the fixed scroll, a muffler provided to cover the discharge port at an upper part of the fixed scroll, and a heat-insulating member provided between the fixed scroll and the muffler. After a refrigerant gas taken into the intake chamber is compressed by the revolving scroll revolving and the compression chamber moving while changing a volume of the compression chamber, the refrigerant gas is discharged from the discharge port. The refrigerant gas discharged from the discharge port is discharged into a muffler space formed by the muffler. The heat-insulating member includes a heat-insulating member discharge port provided in a portion facing the discharge port, a lead valve provided on a surface, of the heat-insulating member, on a side opposite to a side facing the fixed scroll, and a recess provided on the surface, of the heat-insulating member, facing the fixed scroll and provided in a 360-degree area in a circumferential direction facing the intake chamber.

By so doing, a high-temperature and high-pressure refrigerant gas compressed in the compression chamber is discharged from the heat-insulating member discharge port into the muffler space. As a result, the high-temperature and high-pressure refrigerant gas discharged into the muffler space gives an influence of heat from the muffler space into the intake chamber. However, against the influence of heat, the heat-insulating member provided between the fixed scroll and the muffler serves as a heat-insulating layer. Further, since a refrigerant gas and oil in the refrigerant gas intrude into the recess provided in the heat-insulating member and stay in the recess, the recess serves as a second heat-insulating layer. These double heat-insulating layers suppress the influence of heat from the muffler space through which a highest-temperature and highest-pressure refrigerant passes into the intake chamber and compression chamber before compression starts when the fixed scroll has a lowest temperature. In particular, the recess is provided in a 360-degree area, of the heat-insulating member, in a circumferential direction on a surface facing the fixed scroll. Therefore, the influence of heat from the muffler space is extensively and effectively suppressed over a substantially whole area of the intake chamber and the compression chamber continued to the intake chamber. Moreover, together with the muffler space, the heat-insulating member suppresses the influence of heat from a high-temperature refrigerant in a space inside a container above the muffler space into the compression chamber. Accordingly, since an increase in a temperature of the refrigerant is strongly suppressed, a decrease in a circulation amount of the refrigerant is prevented, and an increase in a compression loss of the refrigerant is suppressed. As a result, a highly efficient compressor can be achieved.

In a second aspect of the present disclosure, the heat-insulating member may have a configuration in which at least one of a rim of the heat-insulating member discharge port provided corresponding to the discharge port and an opening edge of the recess has a protruding shape most protruding toward a side of the fixed scroll.

By so doing, a portion having the protruding shape of the heat-insulating member comes into pressure contact with the upper surface of the fixed scroll. Accordingly, an area between the discharge port and the recess is strongly blocked. This prevents a decrease in a heat insulation effect by the recess due to a circulation action generated between a high-temperature and high-pressure refrigerant inside the discharge port and a refrigerant inside the recess. As a result, a high heat insulation effect by the recess is maintained. Therefore, the effect of prevention of a decrease in the circulation amount of the refrigerant due to an increase in the temperature of the refrigerant, and the effect of suppression of an increase in the compression loss of the refrigerant are further enhanced. As a result, a highly efficient compressor can be achieved.

In a third aspect of the present disclosure, a portion close to the heat-insulating member discharge port of the heat-insulating member may be fixed to the fixed scroll by a bolt.

By so doing, the rim of the heat-insulating member discharge port comes into close contact with the fixed scroll. Accordingly, airtightness between the discharge port from which the highest-temperature and highest-pressure refrigerant is discharged and the recess improves. This prevents a decrease in the heat insulation effect by the recess due to the circulation between the high-temperature and high-pressure refrigerant inside the discharge port and the refrigerant inside the recess. Accordingly, the high heat insulation effect by the recess is maintained. Therefore, the effect of prevention of a decrease in the circulation amount of the refrigerant due to an increase in the temperature of the refrigerant, and the effect of suppression of an increase in the compression loss of the refrigerant are further enhanced.

As a result, a highly efficient compressor can be achieved.

In a fourth aspect of the present disclosure, the heat-insulating member may be formed of a porous material such as sintered metal.

By so doing, the heat-insulating member has low heat conductivity. Accordingly, the heat insulation effect of the heat-insulating member is enhanced. As a result, the influence of heat from a high-temperature and high-pressure refrigerant in the muffler space, and the influence of heat from a refrigerant inside the container above the muffler space are further strongly suppressed. Therefore, a decrease in the circulation amount due to an increase in the temperature of the refrigerant is effectively suppressed, and an increase in the compression loss of the refrigerant is suppressed. As a result, a highly efficient compressor can be achieved.

In a fifth aspect of the present disclosure, a plurality of plates may be laminated to form the heat-insulating member.

By so doing, in the heat-insulating member, heat conduction decreases between the respective plates. Accordingly, the heat insulation effect of the heat-insulating member is enhanced. As a result, the influence of heat from the high-temperature and high-pressure refrigerant in the muffler space, and the influence of heat from the refrigerant inside the container above the muffler space are further strongly suppressed. Moreover, among the plurality of plates, when a thickness of plates facing the fixed scroll is thin, the plates facing the fixed scroll have high adhesion to the upper surface of the fixed scroll. As a result, the circulation between the refrigerant inside the recess and the high-temperature and high-pressure refrigerant inside the discharge port is more reliably prevented. Therefore, a decrease in a circulation amount due to an increase in the temperature of the refrigerant is effectively suppressed, and an increase in the compression loss of the refrigerant is suppressed. As a result, a highly efficient compressor can be achieved.

In a sixth aspect of the present disclosure, the plurality of plates may include a plate having a recess.

By so doing, a heat-insulating member having a recess is formed without performing cutting and the like. Moreover, among the plurality of plates, when a thickness of plates facing the fixed scroll is thin, the plates having a recess have high adhesion to the fixed scroll. As a result, the circulation between the refrigerant inside the recess and the high-temperature and high-pressure refrigerant inside the discharge port is strongly prevented. Therefore, a decrease in the circulation amount of the refrigerant due to an increase in the temperature is more efficiently prevented, and an increase in the compression loss of the refrigerant is suppressed. As a result, a highly efficient compressor can be achieved.

Hereinafter, an exemplary embodiment of the present disclosure will be described in detail with reference to the drawings. Note that this exemplary embodiment does not limit the present disclosure.

FIRST EXEMPLARY EMBODIMENT

FIG. 1 is a view showing one example of a cross section of compressor 50 according to a first exemplary embodiment of the present disclosure viewed from a side. FIG. 2 is a view showing one example of a main part of compressor 50. Part (a) of FIG. 2 is a sectional view, and part (b) of FIG. 2 is a detailed view showing one example of a configuration of a heat-insulating member and a fixed scroll. FIG. 3 is a plan view showing one example of a configuration of compressor 50. Part (a) of FIG. 3 is a plan view showing one example of heat-insulating member 24 of compressor 50. Part (b) of FIG. 3 is a plan view showing one example of compression chamber 9 of compressor 50.

FIG. 4 is a view showing one example of heat-insulating member 24 of compressor 50. Part (a) of FIG. 4 is a plan view. Part (b) of FIG. 4 is a view showing one example of a cross section. Part (c) of FIG. 4 is a bottom view.

As shown in FIG. 1, compressor 50 of the present exemplary embodiment includes airtight container 1, compression mechanism 2 disposed inside airtight container 1, and electric motor 3 disposed inside airtight container 1.

Main bearing member 4 is fixed inside airtight container 1 by welding, shrinkage fitting, or the like. Shaft 5 is supported by main bearing member 4.

Fixed scroll 6 is bolted to an upper part of main bearing member 4. Revolving scroll 7 meshed with fixed scroll 6 is inserted between fixed scroll 6 and main bearing member 4 so as to configure scroll compression mechanism 2.

Rotation retaining mechanism 8 including an Oldham ring or the like that prevents rotation of revolving scroll 7 and guides revolving scroll 7 to have a circular orbit motion is provided between revolving scroll 7 and main bearing member 4.

Rotation retaining mechanism 8 causes revolving scroll 7 to have a circular orbit motion by eccentrically driving revolving scroll 7 by eccentric shaft 5 a on an upper end of shaft 5. By so doing, compression chamber 9 formed between fixed scroll 6 and revolving scroll 7 moves from an outer circumferential side toward a central part while contracting a volume of compression chamber 9. Through using of this motion, a refrigerant gas is taken in from intake pipe 10 continued to a refrigeration cycle outside airtight container 1 through intake chamber 11 provided in the fixed scroll between intake pipe 10 and compression chamber 9 and always having an intake pressure. The refrigerant gas taken in is compressed after being confined in compression chamber 9. The refrigerant gas that has reached a prescribed pressure pushes and opens lead valve 13 and is discharged from discharge port 12 in a central part of fixed scroll 6.

The refrigerant gas that has been discharged after pushing and opening lead valve 13 is discharged into muffler space 14, and is sent to the refrigeration cycle from discharge pipe 17 through space inside container 15 of airtight container 1. Note that muffler space 14 is formed by muffler 16 whose circumference is fixed by fixed scroll 6, and covers discharge port 12 and lead valve 13.

On the other hand, pump 18 is provided on a lower end of shaft 5 that revolves and drives revolving scroll 7. A suction port of pump 18 is disposed so as to exist inside oil storage unit 19. Pump 18 operates concurrently with a scroll compressor. Therefore, pump 18 reliably pumps up oil in oil storage unit 19 provided at a bottom of airtight container 1 regardless of a pressure condition and an operation speed.

The oil pumped up by pump 18 is supplied to compression mechanism 2 through oil supply hole 20 that penetrates through an inside of shaft 5. Before or after the oil is pumped up by pump 18, a foreign matter is removed from the oil by an oil filter or the like. This prevents the foreign matter from being mixed into compression mechanism 2. As a result, reliability of compression mechanism 2 can be improved.

Pressure of the oil led to compression mechanism 2 is approximately equivalent to a discharge pressure of the scroll compressor. Moreover, the pressure of the oil led to compression mechanism 2 also serves as a back pressure source for revolving scroll 7. By so doing, revolving scroll 7 stably exerts a prescribed compression function without leaving from or coming into deviated contact with fixed scroll 6. Moreover, a part of the oil intrudes into a fitting portion between eccentric shaft 5 a and revolving scroll 7, and bearing 21 between shaft 5 and main bearing member 4, as though the oil has tried to find a place to escape by a supply pressure and a weight of the oil, and drops after lubricating the respective portions, to return to oil storage unit 19.

Another part of the oil supplied from oil supply hole 20 to high pressure area 22 intrudes into back pressure chamber 23 in which rotation retaining mechanism 8 is located through route 7 a formed by revolving scroll 7 and having a one-opening end in high pressure area 22. The intruded oil plays a role of applying a back pressure to revolving scroll 7 in back pressure chamber 23 in addition to lubrication of a thrust sliding unit and a sliding unit of rotation retaining mechanism 8.

As described above, the refrigerant gas to be compressed in compression mechanism 2 is compressed after being taken into compression chamber 9 between fixed scroll 6 and revolving scroll 7 via intake chamber 11 provided in fixed scroll 6. However, the refrigerant gas to be compressed by compression mechanism 2 is affected by heat of a highest-temperature and highest-pressure refrigerant gas that is discharged from discharge port 12 of fixed scroll 6 into muffler space 14.

Therefore, in the present disclosure, heat-insulating member 24 having a plate shape is provided between fixed scroll 6 and muffler 16, and heat-insulating member 24 is configured so as to be located between muffler space 14 and intake chamber 11. Moreover, on a surface on a side of fixed scroll 6 in heat-insulating member 24, recess 27 (see FIGS. 3 and 4) is provided in a 360-degree area (range) in a circumferential direction facing intake chamber 11.

Here, the 360-degree area in the circumferential direction means that when the surface on the side of fixed scroll 6 of heat-insulating member 24 is viewed from a front, recess 27 is formed at 360° around a substantially center part, that is, along a whole circumference. Note that in a case of FIG. 3, recess 27 has a portion having a substantially annular shape and a portion protruding from the substantially annular portion, but the present disclosure is not limited to this example.

Recess 27 is connected to space inside container 15 (see FIG. 2) via recess groove 27 a.

Note that in a position, of heat-insulating member 24, facing discharge port 12 of fixed scroll 6, heat-insulating member discharge port 25 is formed. On a surface, of heat-insulating member 24, opposite to the surface facing fixed scroll 6, lead valve 13 that opens and closes heat-insulating member discharge port 25 is provided.

Moreover, bolts (not shown) are inserted into holes 26 provided on an outer circumferential portion to fix heat-insulating member 24 to fixed scroll 6 together with muffler 16.

In compressor 50 of the present exemplary embodiment configured as described above, a high-temperature and high-pressure refrigerant gas compressed in compression chamber 9 is discharged from heat-insulating member discharge port 25 of heat-insulating member 24 into muffler space 14. By so doing, the high-temperature and high-pressure refrigerant gas discharged into muffler space 14 gives an influence of heat upon intake chamber 11 from muffler space 14.

At this time, heat-insulating member 24 is located between intake chamber 11 of fixed scroll 6 and muffler space 14, and serves as a heat-insulating layer. By so doing, the influence of heat of the high-temperature and high-pressure refrigerant inside muffler space 14 upon intake chamber 11 is suppressed.

Moreover, recess 27 is formed in heat-insulating member 24. A high-temperature and high-pressure refrigerant released into space inside container 15 and oil inside the refrigerant intrude into recess 27 via recess groove 27 a and stay in recess 27. By so doing, recess 27 has a lower temperature than the highest-temperature and highest-pressure refrigerant inside muffler space 14. Therefore, the stay of the refrigerant and oil inside recess 27 serves as a second heat-insulating layer. By so doing, a first heat insulation action by heat-insulating member 24 and a second heat insulation action in recess 27 are combined together to exert a powerful heat insulation effect.

In particular, recess 27 is provided over the 360-degree area in the circumferential direction on the surface facing fixed scroll 6 of heat-insulating member 24. Therefore, the influence of heat from muffler space 14 is extensively and effectively suppressed over a substantially whole area of intake chamber 11 and compression chamber 9 continued to intake chamber 11.

As a result, an increase in the temperature of a refrigerant in intake chamber 11 and compression chamber 9 by the influence of heat from the refrigerant inside muffler space 14 is strongly suppressed. Accordingly, a decrease in a circulation amount of the refrigerant is prevented, volume efficiency improves, and an increase in a compression loss of the refrigerant is suppressed. As a result, a highly efficient compressor can be achieved.

Moreover, in the present exemplary embodiment, together with muffler space 14, heat-insulating member 24 suppresses the influence of heat from the high-temperature refrigerant in space inside container 15 above the muffler space upon fixed scroll 6. As a result, the temperature of fixed scroll 6 is maintained low. From this perspective, a decrease in the circulation amount of the refrigerant due to an increase in the temperature of the refrigerant is prevented, the volume efficiency improves, and an increase in the compression loss of the refrigerant is suppressed. As a result, a highly efficient compressor can be achieved.

Here, in the present exemplary embodiment, as one example, heat-insulating member 24 is formed of sintered metal. Therefore, an increase in the temperature of the refrigerant is efficiently suppressed. Sintered metal has low heat conductivity and a large number of micro spaces. Since sintered metal has high heat insulation, heat-insulating member 24 formed of sintered metal can efficiently suppress the influence of heat from the high-temperature refrigerant in muffler space 14 and space inside container 15.

Through forming of heat-insulating member 24 with sintered metal, the heat insulation effect by heat-insulating member 24 is enhanced. Accordingly, an increase in the temperature of the refrigerant is more efficiently suppressed, a decrease in the circulation amount of the refrigerant is prevented, and an increase in the compression loss of the refrigerant is suppressed. As a result, a highly efficient compressor can be achieved.

Note that a material of heat-insulating member 24 is not limited to a porous material such as sintered metal. For example, as long as the material has low heat conductivity, any material such as a resin material can be used.

Moreover, heat-insulating member 24 may be one sheet, or may be configured through lamination of a plurality of plates. In laminated heat-insulating member 24 configured through lamination of the plurality of plates, heat conduction between the respective plates is strongly suppressed. Therefore, the heat insulation effect improves and thus this configuration is effective. Moreover, among the plurality of plates configuring heat-insulating member 24, when a thickness of plates facing fixed scroll 6 is thin, for example, when the thickness is as thin as approximately 1 mm, adhesion of the plates facing fixed scroll 6 to an upper surface of fixed scroll 6 improves. Accordingly, circulation between the refrigerant inside recess 27 and the high-temperature and high-pressure refrigerant inside discharge port 12 is more reliably prevented. As a result, the heat insulation action by recess 27 is more effectively exerted.

Note that in the present exemplary embodiment, heat-insulating member 24 is a member having a prescribed shape in advance. Heat-insulating member 24, however, may be formed, for example, between fixed scroll 6 and muffler space 14 by injection molding.

Moreover, bolts are inserted into holes 26 provided on the outer circumferential portion of heat-insulating member 24 to fix heat-insulating member 24 to fixed scroll 6 together with muffler 16. However, a portion close to heat-insulating member discharge port 25 is preferably further fixed to fixed scroll 6 by bolts.

By so doing, the rim of heat-insulating member discharge port 25 comes into close contact with fixed scroll 6 and an area between discharge port 12 and recess 27 is strongly blocked. Accordingly, airtightness between discharge port 12 from which the highest-temperature and highest-pressure refrigerant is discharged and recess 27 improves. As a result, a decrease in the heat insulation effect of recess 27 due to the circulation between the high-temperature and high-pressure refrigerant discharged from discharge port 12 of fixed scroll 6 and the refrigerant inside recess 27 is prevented. As a result, a high heat insulation effect by recess 27 is maintained, a decrease in the circulation amount due to an increase in the temperature of the refrigerant is efficiently prevented, and an increase in the compression loss of the refrigerant is suppressed. As a result, a highly efficient compressor can be achieved.

Moreover, in heat-insulating member 24, the rime of heat-insulating member discharge port 25 provided corresponding to discharge port 12 of fixed scroll 6 has protruding shape 28 (see FIG. 2) most protruding toward the side of the fixed scroll. Therefore, a portion having protruding shape 28 strongly comes into pressure contact with the upper surface of fixed scroll 6. Accordingly, an area between discharge port 12 and recess 27 is strongly blocked. Therefore, a decrease in the heat insulation action by the refrigerant and oil inside recess 27 due to the circulation between the high-temperature and high-pressure refrigerant inside discharge port 12 and the refrigerant inside recess 27 is more reliably prevented. By so doing, the heat insulation effect by recess 27 improves. As a result, the influence of heat by the high-temperature refrigerant inside muffler space 14 is further strongly suppressed. Accordingly, a decrease in the circulation amount due to an increase in the temperature of the refrigerant is more effectively prevented, and an increase in the compression loss of the refrigerant is suppressed. As a result, a highly efficient compressor can be achieved.

Note that, for example, instead of the rim of heat-insulating member discharge port 25, an opening edge on a side of the upper surface of the fixed scroll of recess 27 may have protruding shape 28. This means that at least one of the rim of heat-insulating member discharge port 25 and the opening edge on the side of the upper surface of the fixed scroll of recess 27 may have protruding shape 28. Moreover, through combination of provision of protruding shape 28 and fixing of a bolt in the rim of heat-insulating member discharge port 25, intrusion of the high-temperature and high-pressure refrigerant into recess 27 is more reliably prevented and thus this configuration is effective.

Moreover, since heat-insulating member 24 is configured through lamination of plates provided with recess 27 and plates without a recess, recess 27 is formed without performing cutting. Therefore, heat-insulating member 24 can be provided at a low cost. In addition, since the plurality of plates provided with recess 27 and the plurality of plates without a recess are alternatively laminated, a plurality of recesses 27 is formed in a lamination direction. As a result, the heat insulation effect by recess 27 is further enhanced.

Note that the influence of heat from muffler space 14 and space inside container 15 into intake chamber 11 and compression chamber 9 is further suppressed through formation of a heat-insulating layer on heat-insulating member 24 and muffler 16. Examples of the heat-insulating layer include resin coating, and coating processing including hollow beads whose inside is vacuum or air. However, the heat-insulating layer is not limited to these examples.

As illustrated with reference to the exemplary embodiment described above, the present disclosure can achieve a highly efficient compressor by suppressing an increase in the temperature of the refrigerant, preventing a decrease in the circulation amount of the refrigerant, and suppressing an increase in the compression loss of the refrigerant. The present disclosure, however, is not limited to this exemplary embodiment. This means that the exemplary embodiment disclosed this time should be considered as illustrative in all respects and not restrictive. The scope of the present disclosure is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

INDUSTRIAL APPLICABILITY

As described above, the present disclosure achieves a highly efficient compressor by suppressing an increase in a temperature of a refrigerant, preventing a decrease in a circulation amount of the refrigerant, and suppressing an increase in a compression loss of the refrigerant. As a result, the present disclosure can be widely used for various equipment using a refrigeration cycle.

REFERENCE MARKS IN THE DRAWINGS

-   1, 107: airtight container -   2: compression mechanism -   3: electric motor -   4: main bearing member -   5: shaft -   5 a: eccentric shaft -   6, 102: fixed scroll -   7: revolving scroll -   7 a: route -   8: rotation retaining mechanism -   9, 103: compression chamber -   10, 101: intake pipe -   11: intake chamber -   12, 104: discharge port -   13: lead valve -   14, 106: muffler space -   15: space inside container -   16, 105: muffler -   17, 108: discharge pipe -   18: pump -   19: oil storage unit -   20: oil supply hole -   21: bearing -   22: high pressure area -   23: back pressure chamber -   24: heat-insulating member -   25: heat-insulating member discharge port -   26: hole -   27: recess -   27 a: recess groove -   28: protruding shape -   50: compressor 

1. A compressor comprising: a fixed scroll and a revolving scroll configuring a compression mechanism; a compression chamber formed between the fixed scroll and the revolving scroll; an intake chamber provided on an outer circumferential side of the fixed scroll; a discharge port provided in a central part of the fixed scroll; a muffler provided to cover the discharge port at an upper part of the fixed scroll; and a heat-insulating member provided between the fixed scroll and the muffler, wherein after a refrigerant gas taken into the intake chamber is compressed by the revolving scroll revolving and the compression chamber moving while changing a volume of the compressor, the refrigerant gas is discharged from the discharge port, the refrigerant gas discharged from the discharge port is discharged into a muffler space formed by the muffler, and the heat-insulating member includes a heat-insulating member discharge port provided in a portion facing the discharge port, a lead valve provided on a surface, of the heat-insulating member, on a side opposite to a side facing the fixed scroll, and a recess provided on the surface, of the heat-insulating member, facing the fixed scroll and provided in a 360-degree area in a circumferential direction facing the intake chamber.
 2. The compressor according to claim 1, wherein in the heat-insulating member, at least one of a rim of the heat-insulating member discharge port provided corresponding to the discharge port and an opening edge of the recess has a protruding shape most protruding toward a side of the fixed scroll.
 3. The compressor according to claim 1, wherein a portion close to the heat-insulating member discharge port of the heat-insulating member is fixed to the fixed scroll by a bolt.
 4. The compressor according to claim 1, wherein the heat-insulating member is formed of a porous material such as sintered metal.
 5. The compressor according to claim 1, wherein a plurality of plates is laminated to form the heat-insulating member.
 6. The compressor according to claim 5, wherein the plurality of plates includes plates having the recess. 